WO2017141699A1 - Ensemble couvercle d'embrayage - Google Patents

Ensemble couvercle d'embrayage Download PDF

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Publication number
WO2017141699A1
WO2017141699A1 PCT/JP2017/003517 JP2017003517W WO2017141699A1 WO 2017141699 A1 WO2017141699 A1 WO 2017141699A1 JP 2017003517 W JP2017003517 W JP 2017003517W WO 2017141699 A1 WO2017141699 A1 WO 2017141699A1
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WO
WIPO (PCT)
Prior art keywords
clutch cover
diaphragm spring
cover assembly
clutch
flywheel
Prior art date
Application number
PCT/JP2017/003517
Other languages
English (en)
Japanese (ja)
Inventor
徹 ▲浜▼口
林　大介
Original Assignee
アイシン精機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン精機株式会社 filed Critical アイシン精機株式会社
Priority to DE112017000320.2T priority Critical patent/DE112017000320B4/de
Publication of WO2017141699A1 publication Critical patent/WO2017141699A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/583—Diaphragm-springs, e.g. Belleville
    • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate

Definitions

  • the present invention relates to a clutch cover assembly that presses and separates a clutch disk from an engine flywheel.
  • the clutch cover assembly is mounted on the engine flywheel and used to transmit the driving force of the engine to the transmission side.
  • a clutch cover assembly generally includes a clutch cover fixed to the flywheel, a pressure plate capable of pressing a clutch disc against the flywheel, and a diaphragm spring that urges the pressure plate toward the flywheel. ing.
  • the diaphragm spring is composed of an annular elastic portion and a plurality of lever portions extending radially inward from the inner peripheral edge of the annular elastic portion, and releases a pressure on the pressure plate as well as a function of pressing the pressure plate. It has a lever function.
  • the load characteristic of such a diaphragm spring has a peak portion in which the pressing load at the time of clutch engagement increases as the clutch disk wear increases within the effective use range. For this reason, when the clutch disk is worn, a large load is required to perform the release operation, and the pedal force of the clutch pedal is increased.
  • Japanese Patent Application Laid-Open No. 2008-128260 proposes a clutch cover assembly including a cone spring that generates a load that counteracts the urging force of the diaphragm spring in order to suppress an increase in the release load when the clutch disk is worn.
  • This conventional clutch cover assembly includes a plate that supports a diaphragm spring, and a cone spring that is disposed on the flywheel side of the diaphragm spring and is sandwiched between the diaphragm spring and the plate when the clutch is engaged.
  • the peak portion of the load characteristic of the cone spring is superimposed on the peak portion of the load characteristic of the diaphragm spring in the opposite direction, and as a result, a flat portion is obtained in the combined load.
  • the conventional clutch cover assembly requires two parts, a cone spring and a plate, in order to suppress an increase in release load when the clutch disk is worn. For this reason, the dimensional tolerance of each part is accumulated, and a relative assembly error of each part is added, so that the effect of suppressing the increase in release load is likely to vary greatly. In other words, in order to stably suppress an increase in the release load when the clutch disk is worn, high dimensional accuracy and high-quality assembly of each component are required, and the cost increases.
  • An object of the present invention is to provide a clutch cover assembly that can reduce variations in the effect of suppressing an increase in release load when the clutch disk is worn.
  • a clutch cover assembly comprises: A clutch cover fixed to the engine flywheel; A pressure plate arranged so as to be movable in the axial direction with respect to the clutch cover, and capable of pressing a clutch disc against the flywheel; A diaphragm spring supported by the clutch cover and biasing the pressure plate toward the flywheel; The diaphragm spring is disposed on the flywheel side and supports the diaphragm spring, and is provided integrally with the support portion on a radially outer side of the support portion, and applies a load against the urging force of the diaphragm spring.
  • a support plate having an elastic portion to be generated; A connecting member that connects the support plate and the clutch cover; Is provided.
  • the support portion and the elastic portion are integrally provided on the support plate, the support portion functions as a fulcrum for elastic deformation of the diaphragm spring, and the elastic portion is attached to the diaphragm spring.
  • the elastic portion may have a portion having a nonlinear spring characteristic in which the amount of increase in the load decreases as the deflection increases.
  • the peak portion of the non-linear load characteristic of the elastic portion is superimposed on the peak portion of the load characteristic of the diaphragm spring in the opposite direction, and a flat portion is obtained in the combined load.
  • the elastic portion includes an annular portion that can contact the diaphragm spring, and a plurality of radial connecting portions that connect the annular portion and the support portion,
  • the radial connecting portion has a shape that is curved so that the end portion on the annular portion side warps toward the diaphragm spring side, and is deformed in response to the annular portion being pushed by the diaphragm spring. It may be reversible. According to such an aspect, since the elastic portion can be reversed at the operation limit, it is possible to easily realize a nonlinear spring characteristic in which the amount of increase in load decreases as the deflection increases.
  • the elastic portion includes an annular portion in which a plurality of square holes are formed at intervals in the circumferential direction and a circumferential connection that connects two sides of each square hole that are separated in the circumferential direction.
  • Each circumferential direction connecting portion has a shape that is curved so that the center portion swells toward the diaphragm spring side, and the top portion of the curved shape is deformed in response to being pushed by the diaphragm spring. And may be reversible at the operating limit. Also according to such an aspect, since the elastic portion can be reversed at the operation limit, it is possible to easily realize a nonlinear spring characteristic in which the load increase amount decreases as the deflection increases.
  • a meat relief hole may be formed on the outer side in the circumferential direction of each square hole in the annular portion.
  • the meat relief hole can be deformed so as to be crushed in the circumferential direction when the top of the circumferential connecting portion is pushed by the diaphragm spring. Thereby, the bending of a circumferential direction connection part is promoted. Therefore, by adjusting the size and shape of the meat relief hole, a desired nonlinear spring characteristic can be imparted to the elastic portion.
  • the elastic portion includes an annular portion that can contact the diaphragm spring, and a plurality of radial connecting portions that connect the annular portion and the support portion
  • the radial connection portion includes a pair of beam portions parallel to each other, and a curved portion provided between the pair of beam portions and curved so that a center portion swells toward the flywheel side, and the curved portion is
  • the annular portion may be deformed in response to being pushed by the diaphragm spring and can be reversed at the operation limit. Also according to such an aspect, since the elastic portion can be reversed at the operation limit, it is possible to easily realize a nonlinear spring characteristic in which the load increase amount decreases as the deflection increases.
  • the plurality of radial connecting portions may be provided at equal intervals in the circumferential direction. According to such an aspect, it can suppress that the nonlinear spring characteristic of an elastic part arises in the circumferential direction.
  • the plurality of circumferential connecting portions may be provided at equal intervals in the circumferential direction. Also according to such an aspect, it is possible to suppress the occurrence of variation in the circumferential direction in the nonlinear spring characteristics of the elastic portion.
  • FIG. 1 is a schematic plan view of a clutch cover assembly according to a first embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional view taken along line AA of the clutch cover assembly shown in FIG. 1, and is a longitudinal sectional view in a clutch engaged state (at the time of initial operation).
  • FIG. 3 is a longitudinal sectional view taken along line AA of the clutch cover assembly shown in FIG. 1, and is a longitudinal sectional view in a clutch disengaged state.
  • FIG. 4 is a longitudinal sectional view taken along line AA of the clutch cover assembly shown in FIG. 1, and is a longitudinal sectional view in a clutch engaged state (when the clutch is worn).
  • FIG. 5A is an enlarged perspective view showing an elastic portion when the support plate of the clutch cover assembly shown in FIG.
  • FIG. 5B is a longitudinal sectional view of the support plate shown in FIG. 5A.
  • 6A is an enlarged perspective view showing an elastic portion immediately before an operation limit of a support plate of the clutch cover assembly shown in FIG. 6B is a longitudinal sectional view of the support plate shown in FIG. 6A.
  • FIG. 7A is an enlarged perspective view showing an elastic portion at the operation limit of the support plate of the clutch cover assembly shown in FIG. 1.
  • FIG. 7B is a longitudinal sectional view of the support plate shown in FIG. 7A.
  • FIG. 8 is a schematic plan view of a clutch cover assembly according to the second embodiment of the present invention.
  • FIG. 9 is an enlarged perspective view showing the elastic portion when the support plate of the clutch cover assembly shown in FIG. 8 is initially operated.
  • FIG. 9 is an enlarged perspective view showing the elastic portion when the support plate of the clutch cover assembly shown in FIG. 8 is initially operated.
  • FIG. 10 is an enlarged perspective view showing the elastic portion at the operation limit of the support plate of the clutch cover assembly shown in FIG.
  • FIG. 11 is a schematic plan view of a clutch cover assembly according to the third embodiment of the present invention.
  • FIG. 12 is an enlarged perspective view showing an elastic portion when the support plate of the clutch cover assembly shown in FIG. 11 is initially operated.
  • 13 is a longitudinal sectional view of the support plate shown in FIG.
  • FIG. 14 is a graph for explaining a change in the release load when the clutch disk is worn.
  • FIG. 1 is a schematic plan view of the clutch cover assembly according to the first embodiment.
  • 2 to 4 are longitudinal sectional views taken along the line AA of the clutch cover assembly shown in FIG. 1, and
  • FIG. 2 is a longitudinal sectional view in a clutch engaged state (at the time of initial operation).
  • FIG. 4 is a longitudinal sectional view in a clutch disengaged state, and
  • FIG. 4 is a longitudinal sectional view in a clutch engaged state (when the clutch is worn).
  • the clutch cover assembly 10 is a device that presses and separates the clutch disk 32 from the flywheel 31 of the engine.
  • the clutch cover assembly 10 includes a clutch cover 11 that is fixed to the flywheel 31, a pressure plate 12 that is disposed so as to be movable in the axial direction with respect to the clutch cover 11, and that can press the clutch disc 32 against the flywheel 31;
  • a diaphragm spring 13 is supported by the clutch cover 11 and biases the pressure plate 12 toward the flywheel 31.
  • the clutch cover 11 is a substantially dish-shaped plate member, and includes an outer peripheral portion 11 b fixed to the flywheel 31 and a main body portion 11 a disposed with an axial interval with respect to the flywheel 31. Have.
  • the outer peripheral part 11b of the clutch cover 11 is being fixed to the flywheel 31 with the volt
  • the pressure plate 12 is disposed between the main body portion 11a of the clutch cover 11 and the flywheel 31 so as to oppose the flywheel 31.
  • the pressure plate 12 is attached to the clutch cover 11 by a plurality of strap plates (not shown). Although it is movable in the axial direction, it is connected so as not to be relatively rotatable.
  • a clutch disk 32 is disposed between the pressure plate 12 and the flywheel 31.
  • an annular protrusion 12a is provided on the pressure plate 12 on the main body 11a side so as to protrude in the axial direction.
  • the diaphragm spring 13 is a disk-shaped member disposed between the pressure plate 12 and the main body portion 11 a of the clutch cover 11, and includes an annular elastic portion 13 a that abuts on the protruding portion 12 a of the pressure plate 12, and an annular elastic portion. And a plurality of lever portions 13b extending radially inward from the inner peripheral portion of 13a.
  • a push-type release device (not shown) is in contact with the tip of the lever portion 13b of the diaphragm spring 13. This release device is composed of a release bearing or the like.
  • the diaphragm spring 13 is supported so as to be elastically deformable in the axial direction with respect to the clutch cover 11. More specifically, a plurality of connecting members 15 (for example, supports) are fixed to the main body 11a of the clutch cover 11 by caulking, such as rivets. Further, a support plate 20 that supports the diaphragm spring is fixed to the ends of the plurality of connecting members 15 on the flywheel 31 side by caulking, such as rivets. The inner peripheral portion of the annular elastic portion 13 a of the diaphragm spring 13 is sandwiched between the main body portion 11 a of the clutch cover 11 and the support plate 2 via pivot rings 16 and 17. Thus, the annular elastic portion 13a of the diaphragm spring 13 can be elastically deformed in the axial direction with the pivot rings 16 and 17 on the support plate 20 as fulcrums.
  • a plurality of connecting members 15 for example, supports
  • a support plate 20 that supports the diaphragm spring is fixed to the ends of the plurality of
  • the load gradually decreases, and when the amount exceeds a certain amount of displacement, the load increases gradually. Therefore, in the effective use area, it is a mountain portion (portion protruding upward).
  • symbol L4 has shown the set line in the state in which the clutch disc 32 is not worn out. As wear of the clutch disk 32 increases (the set line moves to the left side of the figure), the load on the diaphragm spring 13 increases.
  • the support plate 20 is provided integrally with the support portion 21 that supports the diaphragm spring 13 and the support portion 21 on the radially outer side of the support portion 21, and applies a load that opposes the urging force of the diaphragm spring 13. And an elastic portion 22 to be generated.
  • the elastic portion 22 is a portion for flattening the load characteristics of the diaphragm spring 13.
  • the elastic portion 22 In the clutch engaged state (at the time of initial operation) shown in FIG. 2, the elastic portion 22 is not worn when the clutch disk 32 is worn. Not compressed (not bent).
  • the elastic portion 22 As the wear of the clutch disk 32 progresses as shown in FIG. 4, the elastic portion 22 is pressed against the flywheel 31 by the diaphragm spring 13 and is deflected to counteract the urging force of the diaphragm spring 13. A load is applied to the diaphragm spring 13. Thereby, even if the wear of the clutch disk 32 progresses, an increase in the release load is suppressed.
  • the elastic portion 22 has a portion having a non-linear spring characteristic, such as a disc spring (cone spring), in which the amount of increase in load decreases as the deflection increases.
  • a broken line with a symbol L2 in FIG. 14 indicates the spring characteristic of the elastic portion 22.
  • the peak portion of the characteristic of the diaphragm spring 13 (see the broken line with the symbol L1) and the peak portion of the characteristic of the elastic portion 22 (see the broken line with the symbol L2) are overlapped in the opposite direction, so that the flat portion in the combined load Is obtained (see the solid line labeled L3).
  • the elastic portion 22 of the present embodiment includes an annular portion 22a that can contact the diaphragm spring 13, an annular portion 22a, and a support as shown in FIG. A plurality of radial direction connecting portions 22 b that connect the portion 21.
  • FIG. 5A is an enlarged perspective view showing the elastic portion 22 at the time of initial operation
  • FIG. 5B is a longitudinal sectional view thereof
  • 6A is an enlarged perspective view showing the elastic portion 22 immediately before the operation limit
  • FIG. 6B is a longitudinal sectional view thereof
  • 7A is an enlarged perspective view showing the elastic portion 22 at the operation limit
  • FIG. 7B is a longitudinal sectional view thereof.
  • reference numeral 24 denotes a connecting member fixing hole.
  • the radial connecting portion 22b is formed from a pair of elongated portions having a curved shape so that the end portion on the annular portion 22a side is warped toward the diaphragm spring 13 side (the lower side in the drawing). Become. As shown in FIGS. 6A and 6B, as the annular portion 22a is pushed by the diaphragm spring and displaced in the axial direction, the radial connecting portion 22b is bent. Then, as shown in FIGS. 7A and 7B, when the radial connecting portion 22b is bent to the operating limit, it is inverted like a hair clip (curved so as to swell toward the diaphragm spring 13).
  • the elastic portion 22 can be reversed at the operation limit, so that the amount of increase in the load decreases as the deflection increases.
  • Non-linear spring characteristics such as a spring can be readily realized.
  • the plurality of radial connecting portions 22b of the elastic portion 22 are provided at equal intervals in the circumferential direction. Therefore, it is possible to suppress the occurrence of variation in the circumferential direction in the nonlinear spring characteristics.
  • the elastic portion 22 has a portion having a non-linear spring characteristic such that the amount of increase in load decreases as the deflection increases, as shown in FIG.
  • the peak portion of the characteristic of the diaphragm spring 13 (see the broken line labeled L1) and the peak portion of the characteristic of the elastic portion 22 (see the broken line labeled L2) are overlapped in the opposite direction and flattened at the combined load. (See the solid line with the symbol L3). Therefore, even if the wear of the clutch disk 32 increases (even if the set line moves to the left side of the drawing), the increase in the release load can be effectively suppressed.
  • the conventional clutch cover assembly requires two parts, a cone spring and a plate, in order to suppress an increase in release load when the clutch disk is worn. For this reason, the dimensional tolerance of each part is accumulated, and a relative assembly error of each part is added, so that the effect of suppressing the increase of the release load when the clutch disk is worn tends to vary greatly. In other words, in order to stably suppress an increase in the release load when the clutch disk is worn, high dimensional accuracy and high-quality assembly of each component are required, which increases costs. In addition, since the cone spring can freely rotate, the cone spring may come into contact with peripheral parts and noise may be generated.
  • the support portion 21 and the elastic portion 22 are integrally provided in the support plate 20, and the number of parts necessary to obtain the effect of suppressing the increase in release load is one part from the conventional two parts. Has been reduced. For this reason, the variation in the release load increase suppressing effect is reduced, and the cost required for component management and assembly is reduced. Moreover, since the elastic part 22 is integral with the support part 21, the movement of the elastic part 22 is restricted, and the generation of noise due to the elastic part 22 coming into contact with peripheral parts is unlikely to occur.
  • the support portion 21 and the elastic portion 22 are integrally provided in the support plate 20, and the support portion 21 functions as a fulcrum in the elastic deformation of the diaphragm spring 13, Since the elastic portion 22 generates a load that opposes the urging force of the diaphragm spring 13, an increase in the release load when the clutch disk is worn is suppressed. Since the number of parts required to obtain the increase suppression effect of the release load is reduced from two conventional parts to one part, the variation in the increase suppression effect of the release load is reduced and the cost required for parts management and assembly Is reduced. Moreover, since the elastic part 22 is integral with the support part 21, the movement of the elastic part 22 is restricted, and the generation of noise due to the elastic part 22 coming into contact with peripheral parts is unlikely to occur.
  • the elastic portion 22 has a portion having a non-linear spring characteristic in which the amount of increase in load decreases as the deflection increases, and therefore, the peak portion of the load characteristic of the diaphragm spring 13
  • the peak portions of the non-linear load characteristics of the elastic portion 22 are overlapped in the opposite direction, and a flat portion is obtained in the combined load. Thereby, the release load when the clutch disc is worn can be effectively suppressed.
  • the elastic part 22 has the annular part 22a which can contact
  • Each of the radial connecting portions 22b has a curved shape so that the end portion on the annular portion 22a side is warped toward the diaphragm spring 13 side, and is deformed as the annular portion 22a is pushed by the diaphragm spring 13, Since reversal is possible at the operating limit, it is possible to easily realize a nonlinear spring characteristic in which the amount of increase in load decreases as the deflection increases.
  • the plurality of radial connecting portions 22b are provided at equal intervals in the circumferential direction, it is possible to suppress the occurrence of variations in the circumferential direction in the nonlinear spring characteristics of the elastic portion.
  • FIG. 8 is a schematic plan view of the clutch cover assembly 100 according to the second embodiment of the present invention.
  • FIG. 9 is an enlarged perspective view showing the elastic portion 122 during the initial operation of the support plate 120 of the clutch cover assembly 100 shown in FIG.
  • the elastic part 122 includes an annular part 122a in which a plurality of square holes 122c are formed at intervals in the circumferential direction, and a circumference of each square hole 122c. And a circumferential connecting portion 122b that connects two sides separated in the direction.
  • Each circumferential connecting portion 122b is composed of a pair of elongated portions having a curved shape so that the central portion swells toward the diaphragm spring 13 (upper side in FIG. 9). In response to the curved top portion of the circumferential connecting portion 122b being pressed against the diaphragm spring 13, the circumferential connecting portion 122b is bent. And as shown in FIG.
  • a meat escape hole 122d is formed on the outer side in the circumferential direction of each square hole 122c in the annular portion 122a.
  • the meat relief hole 122d can be deformed so as to be crushed in the circumferential direction when the top portion of the circumferential connecting portion 122b is pressed by the diaphragm spring 13. Thereby, the bending of the circumferential direction connection part 122b is promoted. Therefore, desired nonlinear spring characteristics can be imparted to the elastic portion 122 by adjusting the size and shape of the meat relief hole 122d.
  • the plurality of circumferential connecting portions 122b of the elastic portion 122 are provided at equal intervals in the circumferential direction. Therefore, it is possible to suppress the occurrence of variation in the circumferential direction in the nonlinear spring characteristics.
  • FIG. 11 is a schematic plan view of a clutch cover assembly 200 according to the third embodiment of the present invention.
  • 12 is an enlarged perspective view showing the elastic portion 222 when the support plate 220 of the clutch cover assembly 200 shown in FIG. 11 is initially operated, and
  • FIG. 13 is a longitudinal sectional view thereof.
  • the elastic portion 222 includes an annular portion 222a that can contact the diaphragm spring, and a plurality of radial directions that connect the annular portion 222a and the support portion 21. And a connecting portion 222b.
  • Each radial connecting portion 222b is provided between a pair of beam portions 222b2 parallel to each other and the pair of beam portions 222b2, and is curved so that the center portion swells toward the flywheel 31 (upper side in FIGS. 12 and 13). And a curved portion 222b1.
  • the curved portion 222b1 of the radial connecting portion 222b is bent in response to the annular portion 222a being pushed by the diaphragm spring 13. And if the bending part 222b1 of the radial direction connection part 222b is bent to an operation limit, it will reverse like a hair clip (it will curve so that it may swell to the diaphragm spring 13 side). As described above, since the elastic portion 222 can be reversed at the operation limit, nonlinear spring characteristics such as a disc spring in which the amount of increase in load decreases as the deflection increases can be easily realized.
  • the plurality of radial connecting portions 222b of the elastic portion 222 are provided at equal intervals in the circumferential direction. Therefore, it is possible to suppress the occurrence of variation in the circumferential direction in the nonlinear spring characteristics.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un ensemble couvercle d'embrayage comportant : un couvercle d'embrayage fixé sur un volant d'inertie d'un moteur ; un plateau de pression disposé de manière à pouvoir se déplacer axialement par rapport au couvercle d'embrayage, le plateau de pression étant capable de pousser un disque d'embrayage contre le volant d'inertie ; un ressort à diaphragme supporté sur le couvercle d'embrayage, le ressort à diaphragme poussant le plateau de pression vers le volant d'inertie ; une plaque de support comportant une partie de support qui est disposée sur le côté volant d'inertie du ressort à diaphragme et qui supporte le ressort à diaphragme, et une partie élastique qui est réalisée d'un seul tenant avec la partie de support sur le côté radialement extérieur de la partie de support et qui produit une charge à l'encontre de la force de sollicitation du ressort à diaphragme ; et un élément de liaison pour relier la plaque de support et le couvercle d'embrayage.
PCT/JP2017/003517 2016-02-19 2017-02-01 Ensemble couvercle d'embrayage WO2017141699A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017000320.2T DE112017000320B4 (de) 2016-02-19 2017-02-01 Kupplungsdeckelanordnung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-030272 2016-02-19
JP2016030272A JP6631306B2 (ja) 2016-02-19 2016-02-19 クラッチカバー組立体

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WO2017141699A1 true WO2017141699A1 (fr) 2017-08-24

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BR102021014397A2 (pt) * 2021-07-21 2023-01-31 Farah Ossaille Nicolau Sistema e processo de gerenciamento de instruções, comunicações e tarefas pré-programadas em um dispositivo eletrônico

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58157030U (ja) * 1982-04-15 1983-10-20 株式会社大金製作所 クラツチカバ−組立体
JPS60101344U (ja) * 1983-12-16 1985-07-10 黒田　哲正 反転スプリング
JPH102348A (ja) * 1996-06-13 1998-01-06 Exedy Corp クラッチカバー組立体

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989001096A1 (fr) * 1987-08-03 1989-02-09 Kabushiki Kaisha Daikin Seisakusho Ensemble cloche d'embrayage
JP2008128260A (ja) * 2006-11-16 2008-06-05 Exedy Corp クラッチカバー組立体
DE102010054288A1 (de) * 2009-12-22 2011-06-30 Schaeffler Technologies GmbH & Co. KG, 91074 Stützfeder

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58157030U (ja) * 1982-04-15 1983-10-20 株式会社大金製作所 クラツチカバ−組立体
JPS60101344U (ja) * 1983-12-16 1985-07-10 黒田　哲正 反転スプリング
JPH102348A (ja) * 1996-06-13 1998-01-06 Exedy Corp クラッチカバー組立体

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JP2017145947A (ja) 2017-08-24
DE112017000320B4 (de) 2020-10-15
JP6631306B2 (ja) 2020-01-15
DE112017000320T5 (de) 2018-10-25

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